Large diameter mooring turret with compliant deck and frame

ABSTRACT

A very large diameter turret for mooring a VLCC class FPSO vessel. A large diameter rail and wheel bearing system is disposed between a turret main deck and the hull of the vessel. The turret is designed for a flexibility to allow the turret main deck to conform to the sag or hog of the vessel so that excessive forces on the wheels of the bearing system are avoided. The turret&#39;s main deck, in a preferred embodiment, includes a center hub, an outer ring, and spokes between the hub and outer ring. A lower chain deck is preferably connected to the main deck by pillars or columns, or alternatively by riser tubes alone, or other structures that achieve the desired flexibility of the main deck.

CROSS REFERENCE TO RELATED APPLICATION

[0001] This non-provisional application is based on ProvisionalApplication Serial No. 60/344,104 filed Dec. 28, 2001, the priority dateof which is claimed for this application.

BACKGROUND OF THE INVENTION

[0002] 1. Field of the Invention

[0003] This invention relates generally to mooring systems for offshorevessels and Floating Production Units (“FPUs”) such as Floating Storageand Offloading vessels (“FSOs”), Floating Production Storage andOffloading vessels (“FPSOs”), Floating Storage Drilling Production andDrilling Units (“FPDSOs”) and in particular to turret mooringarrangements, or systems, where a turret is rotatably supported on thevessel and where the turret is fixed to the sea bed by anchor legs sothat the vessel can weathervane about the turret.

[0004] 2. Description of the Prior Art

[0005] Turret mooring systems have been used for some time for FPUs andespecially with FPSOs. FPSOs are production platforms typicallyconstructed by reconfiguring existing tanker hulls. FPSOs are the mostuseful of FPUs in terms of water depth and sea conditions due to theirvariation in moorings and ship shape configurations. FPSOs are eitherspread moored (anchored directly to the seafloor and unable tocompletely weathervane and rotate around a center point of mooring), orthey are attached to the seafloor via an internal or external rotatableturret that is moored to the seafloor for 360° weathervaning capabilityof the vessel. FIG. 1 is an illustration of a prior art turret mooredFPSOV with the turret connected to the sea floor by groups of anchorlegs L and risers R running from the sea floor to the turret forrotatable coupling to vessel pipes which run to storage holds.

[0006] FPSOs compete with other kinds of floating production units suchas semi-submersibles, spars, and tension leg platforms. These othersystems generally do not have large product storage capacity like FPSOs,but they do have the advantage of easily handling a large number ofrisers (the flexible pipes and control umbilicals connected between theproduction unit and subsea wellheads). Large numbers of risers arerequired for subsea oil fields when it is not desirable to use subseamanifolding connecting several wells together. The number of risers canbe from the twenties to ninety or even more. The spread moored FPSO hasthe advantage of large product storage capacity and also has the spacecapability for large numbers of risers. One main disadvantage of thespread moored FPSO is the reduced availability for tandem offloading dueto occasional bad weather conditions preventing a safe approach of theshuttle tanker to connect to the FPSO. In many locations the roughweather direction changes and can also cause undesirable rolling motionsof the vessel that are problematic to the process equipment and to thecrew. The competitiveness of all of the above floating production unitsdepends on their advantages and disadvantages.

[0007] As mentioned above, the present invention is directed to a turretmooring arrangement, and in particular to a rotatably mounted turret oflarge diameter for the purpose of accommodating a large number of risersand for providing other advantages resulting from a large diametergeostationary turret. Such advantages are summarized below.

[0008] Prior turret mooring arrangements are known in the art thatinclude turrets of small to moderate diameter where the problemsassociated with vessel hull deflections are considered. A moonpool (acylindrical tube extending from top to bottom through a vessel hull) isrequired to contain and usually support the turret bearing and turretshaft. Flexure of the vessel hull due to sea conditions can causeundesirable structural deflections in the moonpool at the foundationsfor the turret bearings. This effect can be substantial and detrimentalfor large moonpool diameters, and unless steps are taken to mitigatesuch effects, the turret bearings will suffer from high concentratedloads.

[0009] Prior turret designers have sought to minimize turret diametersdue to requirements of roller bearing assemblies requiring flat machinedsurfaces not exceeding a predetermined diameter. In such arrangement,designers have sought to isolate the flat bearing races with variouselastic elements and apparatus in an effort to accommodate hulldeflections. Other designers have attempted to provide bearing wheel andrail arrangements for vessel-turret designs. A few of the prior artattempts to solve the problem of vessel hull deflection as it affectsbearing operation is presented below.

[0010] Norwegian Patent No. 165,285 shows a structural suspension thatattempts to provide a satisfactory load distribution around a bearingwheel track that may not be flat. Independent radial arms are disclosedto which vertical and radial load rollers are attached. The radial armsattach to a circular ring that twists to add to the flexibility of thebending beam deflection of the arms. This concept is limited in loadcarrying capacity and limited to relatively small turret diameters.

[0011] U.S. Pat. No. 5,052,322 to Poldervaart illustrates a bearingfixed to a rigid ring that does not follow deformations of the hull ofthe ship. A cylindrical tube supporting the rigid ring tends to flexwith the vessel hull while the bearing and turret remain relativelyisolated from hull deflection. The benefits of this design diminish asthe moonpool (or turret insert tube) diameter and hull deflectionsincrease.

[0012] U.S. Pat. No. 5,515,804 to Pollack shows internal and externalturret bearing arrangements with a generally rigid upper mount includinga resiliently deflectable support structure that includes a plurality ofelastomeric shear pads. These arrangements are also difficult andexpensive to scale up to large diameters due to the proportionallyincreasing size and shear motion capacity of the shear pads.

[0013] U.S. Pat. No. 5,359,957 to Askestad illustrates radial bearingarms connected to a substructure in the turret which provide individualsuspension and can absorb unevenness and deformations in the bearing.Rollers attached to the ends of the radial arms support the turret load.This design is also limited in load carrying capacity by the difficultyof attaching large numbers of rollers for high load capacity.

[0014] U.S. Pat. No. 5,517,937 to Lunde shows a turret arrangement foraccommodating many risers in which the riser tubes are arranged at anangle to minimize the bearing diameter to about eight meters or lesswhile the bottom diameter of the turret is made large in diameter toaccommodate the necessary spacing of the risers below the turret.Minimizing the bearing diameter is one way of mitigating the effects ofthe previously mentioned deflections, but construction complexity andother disadvantages such as limited equipment space inside the turretresult from this arrangement. As the numbers of risers increase, theirweight eventually overcomes the available capacity of the smallerbearing diameters.

[0015] U.S. Pat. No. 5,860,382 to Hobdy illustrates a turret with radialbearing rollers arranged with spring assemblies that allow forunevenness of the radial wheel rail and maintain roller contact withtheir rail. This arrangement of turret and bearing is suitable forrisers numbering thirty to forty, but may not be practical for a muchlarger quantity of risers. The limitation of larger turrets of thisdesign is the low flexibility of the tube-shaped turret structure. Theturret is vertically shear-stiff, and the wheel and rail system musttherefore be designed for significantly increased loading per wheel toaccommodate the out-of-flat condition of the vertically loaded wheelrails.

[0016] U.S. Pat. No. 6,164,233 to Pollack describes bearing devices thatinclude hydraulic cylinders and pistons to support vertical loads thatare arranged to accommodate vessel hull deformations.

[0017] U.S. Pat. No. 6,263,822 to Fontenot shows elastomeric padsarranged radially and vertically around the main bearing which rotatablysupports a mooring turret. This arrangement for shear and compression ofelastomeric pads serves to compensate for hull deflection at the mainbearing. The elastomeric pads accommodate vertical and radialdeflections of the hull. This design is also expensive and may bedifficult to scale upward to a large size.

[0018] U.S. Pat. No. 6,269,762 to Commandeur illustrates a bogie wheelbearing support structure mounted on top of a moonpool tube that extendsabove the connection to the vessel hull to isolate the bearing structurefrom the hull deflections. Commandeur also shows elastically deformableelements (rubber filler) beneath the bogie wheels to help even out theload on the wheels. The very tall moonpool tube also serves to isolateradial hull deflections from the bearing assemblies.

[0019] The advantages of this invention will be more apparent bycomparison to prior art turrets.

[0020]FIG. 2 shows a prior art large turret capable of supporting 43risers that was supplied for a Petrobras Field Development offshore ofBrazil. The illustration is of the turret parts loaded on a barge B fortransport from the fabrication yard. The complex arrangement of thelower turret T can be seen in which the turret structure and all of theriser guide tubes are tapered toward the top end in an effort to reducethe upper bearing diameter. The turret structure is of rigidconstruction.

[0021]FIG. 3 is a drawing of a prior art turret supplied by SOFEC, Inc.for an offshore oil field in the South China Sea. The turret 200 has acylindrical tube structure that is relatively rigid in bending andshear. The upper bearing structure and the turret are rigid in theradial and vertical directions. A spring suspension system supportingthe upper bearing 202 in combination with a heavily reinforced bearingsupport 204 structure allows structural deflections of the vessel at theturret insert tube (moonpool) without overloading the bearing. Thebearing is a three-row roller bearing mounted in a manner similar to theapparatus of U.S. Pat. No. 5,356,321 to Boatman. This turret arrangementis typical of many in the single point mooring industry utilizing acombination of a lower bearing 208 near the vessel keel with an upperbearing 202 located near the main deck of the vessel.

[0022]FIG. 4 is a drawing of a prior art turret designed and supplied bySOFEC, Inc. for an oil field offshore of Brazil. An upper bearingsystem, located near the main deck of the vessel, includes a radialwheel/rail bearing 210 and an axial wheel/rail bearing 212 to providerotational support between the turret and the vessel. No lower radialbearing was provided. A wheel and rail bearing system was provided forthe vertical load to withstand large loads, because hull deflectionsconcentrate the load onto only a fraction of the wheels. The verticalload rollers were designed with sufficient excess capacity per roller tocarry the total load on only a portion of the total number of rollers.Radial wheels mounted on springs that spread the load over many radialwheels accommodates the radial deflections. The turret is stiff in boththe radial and vertical directions.

[0023] For small diameter turrets, an axial roller bearing assembly canbe provided between the turret and the vessel. Such roller bearingassemblies require that the bearing races be flat, machined surfaces.Such races have in the prior art often been isolated from ovaling due tovessel sagging and hogging by various elastic arrangements between alower bearing race and the vessel. As the diameter of the turret becomesvery large, roller bearing assemblies are not feasible due to theinability to machine flat surfaces for the very large diameter.Wheel-rail assemblies can be installed between the turret and thevessel, and described above, but for very large turrets carrying a verylarge number of risers, the forces on certain wheels due to the saggingor hogging of the vessel can become so large as to make it impracticalto provide a very large turret for accepting a very large number ofrisers. The above very large number of risers connotes a number of from40 to 120 risers.

[0024] Summing up, the problems for designing a very large turret (VLT)in the past have been either of vertically and radially stiffconstruction combined with various expensive devices to isolate thebearing, or they are limited in their range of diameter and loadcarrying capacity. The problems associated with a relatively inflexiblestructure limits the economic benefits of a large diameter turret,requires larger bearing capacities, and tends to reduce the wear life ofthe bearings.

[0025] 3. Identification of Objects of the Invention.

[0026] A primary object of the present invention is to provide aneconomical turret arrangement that has inherent structural flexibility,thereby making practical a large diameter main bearing that supports avery large turret.

[0027] Another object of the present invention is to provide aneconomical large diameter turret mooring arrangement for an FPSO thatwill accommodate a very large number of risers (either flexiblenon-metallic pipe or rigid steel pipe flow lines) where the large numberof risers greatly exceeds those presently known in the art.

[0028] Another object of the present invention is to provide a practicalturret configuration of sufficient size that allows a weathervaningvessel to be used as a floating production unit (FPU) with at least asmany risers as can be connected to a non-weathervaning FPU such as aspread moored ship-shaped vessel or a semi-submersible vessel.

[0029] Another object of the present invention is to provide a wheel andrail bearing arrangement for a very large turret (VLT) frameconfiguration that has sufficient flexibility so that vessel hogging andsagging deflection causes a maximum load per wheel to increase not morethan preferably about 50 percent greater than would occur with the railsin a perfectly flat plane, and not exceeding 150 percent greater thanwould occur with the rails in a flat plane.

[0030] Another object of the present invention is to provide a turretwith a flexible structural frame configuration that allows asliding-type lower bearing of a diameter greater than 12 meters diameterto be used near the vessel keel elevation in combination with an upperbearing greater than about 14 meters diameter located near the vesselmain deck.

[0031] Another object of the present invention is to provide a turretwith a flexible structural frame configuration with elastomeric bumperpads attached to the lower turret near the vessel keel elevation incombination with an upper bearing greater than about 14 meters diameterlocated near the vessel main deck.

[0032] Another object of the present invention is to provide a turretwith a flexible structural frame configuration that allows the optionalinstallation of protective riser tubes between the chain table and themain deck without appreciably increasing the stiffness of the turretframe.

SUMMARY OF THE INVENTION

[0033] The objects identified above, as well as other features andadvantages of the invention are provided by a turret configuration inwhich the turret includes an upper section, a lower section, and acoupling structure such as at least three vertical columns or risertubes alone for coupling the upper and lower sections together. Theturret mooring arrangement is rotatably supported on a vessel thatfloats at the surface of the sea and that can weathervane about theturret. The lower section of the turret is anchored by at least threemooring lines that extend to the sea floor for anchoring the turret in asubstantially geostationary position.

[0034] The arrangement utilizes a known bearing system, that is, a wheeland rail system that can be manufactured economically in sizes largerthan 14 meters diameter. The phrase, “very large turret” (VLT), as usedherein, refers to turrets requiring moonpool diameters larger than about14 meters and up to about 35 meters. The moonpool diameter is limitedonly by the available width of the vessel into which the moonpool(turret insert tube) is fitted. The turret frame is configured in a waythat provides sufficient flexibility to allow the turret main deck toconform to the vessel deck flexure shape as the vessel bends in theso-called “hogging and sagging” conditions. The bending flexure of thevessel hull causes the bottom or lower supporting surfaces on the vesselon which the wheels or rollers are supported to elastically flex and notremain in a flat plane. The load carrying frame members of the turretflex in concert with the vessel hull due to turret loads and therebyspread the loads to turret mounted upper rails for the wheels moreuniformly than is possible with a stiff turret frame.

[0035] The upper section of the turret includes an axial/radial bearingassembly. This assembly permits the vessel to weathervane about theturret while resisting loadings caused by weather conditions, includingsea conditions, causing the vessel to heave, pitch, roll, and yaw in thesea. The bearing assembly uses the commercially available Amclyde typeflanged wheel and rail construction that can be manufacturedeconomically for rail sizes larger than 12 meters diameter. The bearingfoundation or support structure attached to the vessel hull bends andflexes with the vessel hull. The main deck of the turret is capable offlexing under the vertical load of the turret weight, mooring legs, andthe weight of the risers and due to its flexible design follows the flexof the vessel. Certain geometric ratios such as main deck thickness todiameter; main deck thickness to depth of vessel hull; and columndiameter to column length are required to be within certain ranges toprovide the required flexibility without causing detrimental largestresses in the frame members.

[0036] The lower section of the turret includes a chain table to whichmooring legs are attached, a structural coupling arrangement such asvertical columns which connect the chain table to the main deck, andriser tubes which protectively enclose the risers between the chaintable and the main deck. An alternative embodiment of the inventionplaces elastomeric bumper units at the outside diameter of the chaintable to occasionally react against the inside of the moonpool.

[0037] Existing tanker vessels in the (Very Large Crude Carrier) VLCCclass are available in the industry for FPSO conversion. The hull widthof the VLCCs range from 50 meters to as much as 70 meters beam width.These vessels, with moonpool diameters of up to about 30 to 35 meters,can accept turrets that are practical according to the invention andthat are large enough to accommodate between forty and one hundredtwenty risers arranged in not more than two concentric rows at thebottom of the turret.

[0038] This invention, as defined below by the claims, makes possible aVery Large Turret (VLT) for a very large crude carrier (VLCC) convertedinto a weathervaning FPSO vessel. A weathervaning vessel is advantageousas compared to a spread moored vessel, because it provides safer shuttletanker mooring for tandem offloading and more up-time for offloading. AVLT, i.e., one capable of handling between forty and one hundred twentyrisers, has many advantages. All such advantages result from the largebearing diameter in combination with a bearing foundation and bearingarrangement which rotatably couples the vessel to a relatively flexibleturret (as compared to prior turrets) capable of conforming to hoggingand sagging deflections of the vessel hull. Advantages of the VLTaccording to the invention are summarized below.

[0039] 1. The increased riser capacity allows a deep water fieldoperator to no longer be required to use subsea manifolding because ofspace limitations on the turret. This feature provides maximumflexibility for field layout.

[0040] 2. The VLT economically provides sufficient space for oversizedriser tubes that allow maximum flexibility in riser location at theturret.

[0041] 3. The increased space on the turret for manifold modules allowsutilization of conventional valves rather than higher cost compactvalues.

[0042] 4. The manifold module can be large enough for choke valves inall production and test situations. This feature allows all productionand test swivels to be of lower pressure rating for higher reliability.

[0043] 5. The manifold space can be large enough for a high pressure gasmanifold to split the gas flow to a reinjection header and to a gassales riser.

[0044] 6. The space on the turret is sufficient for large piglauncher/receivers for instrumented pigs.

[0045] 7. Space on the turret is provided for storing quantities ofchemical injection fluids and pumps. This feature reduces the number ofhigh pressure fluid paths in the swivel stack for the chemicals.

BRIEF DESCRIPTION OF THE DRAWINGS

[0046] The objects, advantages, and features of the invention willbecome more apparent by reference to the drawings that are appendedhereto and wherein like numerals indicate like parts and whereinillustrative embodiments are shown, of which:

[0047]FIG. 1 is an illustration of a prior art FPSO vessel floating onthe sea with anchor legs connected between a seafloor and a rotatablymounted turret on the vessel, with numerous flowlines on the seafloorcoupled to and flexible risers supported from the turret in the floatingvessel; and

[0048]FIGS. 2, 3 and 4 depict prior art turrets and turret mooredvessels as described above;

[0049]FIG. 5 illustrates an embodiment of the invention in a transversecross sectional view of a turret in a vessel, and shows an upper bearinglocated near the main deck of the vessel, but does not include a lowerbearing near the vessel keel;

[0050]FIG. 6A illustrates greatly exaggerated flexure of the turretframe of FIG. 5 when acted upon by horizontal forces on the chain table;

[0051]FIG. 6B illustrates greatly exaggerated flexure of the turretframe of FIG. 5 when acted upon by vertical forces on the chain table;

[0052]FIG. 7A is a sketch of a turret moored vessel showing a greatlyexaggerated example of the vessel in a “sagging” condition with aflexible turret main deck conforming to the shape of the vessel sag;

[0053]FIG. 7B is an exaggerated sketch of the turret of FIG. 7A with aflexible main deck;

[0054]FIG. 7C is a perspective view of a large diameter turret with aflexible turret having a main deck capable of conforming to a sagging ora hogging shape of a supporting surface subject to vessel sag or hog;

[0055]FIG. 8 is a sketch which illustrates wheel loads distributedaround a circular roller track (rail), with a linear load variation thatoccurs when an upper rail of the turret and a bottom rail of the vesselare both in a perfectly flat condition and an external load “Fv” isacting vertically at an eccentric location “e” from the center of thebearing;

[0056]FIG. 9 illustrates wheel loads distributed around a circularroller track (rail) that has been deformed by bending deflection of thevessel hull, and shows that the upper rail attached to a stiff turretdoes not conform to the shape of the roller track on the vessel hull;

[0057]FIG. 10 illustrates wheel loads distributed around circular trackrails that have been deflected by vessel hull bending and shows thatwhere the turret structure above the upper rail is sufficientlyflexible, the upper rail conforms to the out-of-plane shape of the lowerrail;

[0058]FIG. 11 illustrates the basic geometry of the flexible turretframe of a preferred embodiment of the invention and defines certaindimensions used as parameters for turret design;

[0059]FIG. 11A is a graph of the parameter δ/D1 as a function of a ratioA1/D1 with an indication of acceptable ranges of those parameters toachieve a sufficiently flexible turret in order to meet specifiedcharacteristics;

[0060]FIG. 12 is an enlarged view of the upper turret structure of thearrangement illustrated in FIG. 5, showing the bearing system andrelated apparatus;

[0061]FIG. 13 is an enlarged cross section view of the arrangementillustrated in FIG. 5 showing the area at one side of the turret at thebearing and riser supports;

[0062]FIG. 13A illustrates a preferred embodiment wherein the riser tubehangs from the main deck of the turret frame;

[0063]FIGS. 13B, 13C, 13D and 13E illustrate the construction assemblyof riser tubes for a preferred embodiment of this invention;

[0064]FIG. 14 shows an embodiment of the invention with a top plan viewof the turret winch deck of the arrangement illustrated in FIG. 5;

[0065]FIG. 15, is a plan view of the turret main deck of the arrangementillustrated in FIG. 5 where manifold piping and equipment are omittedfrom the view for clarity;

[0066]FIG. 16 shows a plan view of the chain table of the arrangementillustrated in FIG. 5;

[0067]FIG. 17 shows an alternative embodiment of the invention with atransverse cross section view of a turret and vessel and illustrating aflexible frame structure turret supported by an upper bearing at themain deck of the vessel, and by a lower bearing near the vessel keel;

[0068]FIG. 18 shows another embodiment of the invention in a transversecross section view of a turret and vessel, and illustrates a turrethaving a flexible frame structure which is rotatably supported by anupper bearing at the main deck of the vessel, and an elastomeric bumperpad near the vessel keel;

[0069]FIG. 19 shows another embodiment of the invention and shows in anelevation view riser tubes also serving as the structural membersconnecting the chain table to the turret main deck; and

[0070]FIG. 20 shows another embodiment of the invention with atransverse section view of a turret where the turret main deck isconnected to the chain table by a small diameter tube.

DESCRIPTION OF THE INVENTION

[0071] The illustrations of the preferred embodiments of the inventionare described by reference to the Figures briefly described above andinclude reference numbers for the following items: 100 Flexible frameturret 1 Turret main deck 2 Column 3 Chain table 4 Bearing Foundation 5Turret insert tube (Moonpool) 6 Pump deck 7 Manifolds 8 Winch deck 9Winch 10 Swivel stack 11 Swivel torque tube 12 Load wheels 13 Radialwheels 14 Uplift wheels 15 Radial spring assembly 16 Riser tube 17 Riserbend stiffener 18 Riser 19 Chain support 20 Mooring chain 21 Winch line22 Piping 23 Safety valves 24 Riser support clamp 25 Riser tube slipjoint 26 Rail 27 T-Beam 28 Horizontal sheave 29 Moveable vertical sheave30 Vessel main deck 31 Radial beam 32 Center ring 33 Riser support tube34 Outer ring 35 Chemical tank 36 Chemical pump unit 37 Seal 38Elastomeric bumper pad 39 Clearance gap 40 Chain installation deck 41Chain hang-off bracket 42 Lower bearing 43 Vessel hull structure 44Riser tube flange 45 Hanging riser tube 46 Welding fixture 47 Weld joint48 Riser tube collar 49 Riser end fitting 50 Riser tube hole 51 Hullelastic curve 52 Main deck elastic curve 53 Central column

[0072]FIG. 1 illustrates a prior art FPSO V floating on the sea withanchor legs L and numerous flexible risers (i.e., flexible marine hoses)R hanging from the turret to the seafloor. Other known variations ofriser systems including steel catenary and hybrid steel and flexibleriser systems are suitable for the turret of this invention.

[0073]FIG. 5 is a transverse sectional view of one preferred embodimentof the invention. The flexible frame turret 100 comprises three primarycomponents: turret main deck 1; connecting structure such as columns 2;and chain table 3. At least three pillars or columns 2, but preferablysix, connect main deck 1 to chain deck 3 with structural momentconnections that transfer the axial forces and moments from chain table3 to main deck 1. A single pillar or cylindrical structure could besubstituted for pillars or columns 2 between deck 1 and chain table 3.(See FIG. 20) Mooring chain 20 is the upper section of the mooring leg;it is attached to chain table 3 by a pivoting ratchet type chain support19. A radial array including at least three mooring legs, but preferablya total of nine legs in three groups of three legs each, is commonlyused where each leg comprises various known combinations of chain, wirerope, synthetic or polyester rope, all connected together with suitableshackles and fittings to a termination point on the seafloor at anchorsor piles. Chain installation deck 40 provides access to workers tohandle chain during mooring leg installation. The slack end of chain 20is secured to deck 40 by chain hang-off bracket 41 after winch 9 pullsmooring leg 20 to an appropriate tension.

[0074] Risers 18 extend from the sea floor beneath the flexible frameturret 100 and extend through chain table 39 and through riser tubes 16to main deck 1. A riser bend stiffener 17 restrains each riser 18horizontally and transfers horizontal forces of the risers to the chaintable 3. The riser tubes 16 protectively enclose each riser 18 fromchain table 3 to main deck 1.

[0075] When environmental forces cause the vessel to move from itsneutral calm water position, vertical and horizontal mooring restoringforces of anchor legs 20 act on chain table 3 and are transferredthrough pillars or columns 2 (or other suitable structure) to mainturret deck 1, and through three sets of wheels 12, 13, 14, into bearingsupport 4, as shown below by reference to FIGS. 12 and 13. Turret inserttube 5 is a primary load transfer structure attached inside the vesselhull structure 43. Subsea currents, surface wave motions, and vesseloffset motions also cause vertical and horizontal riser forces to act onthe turret. Riser forces are significant because of the great number ofrisers provided. As few as 40 and up to as many as 120 risers 18 arecontemplated for use with the preferred embodiment of the invention.Vertical riser forces of risers 18 are transferred upward through eachriser tube 16 and are primarily reacted by turret main deck 1.Horizontal riser forces are transferred horizontally at chain table 3and are primarily reacted by chain table 3.

[0076]FIG. 6A illustrates the flexible nature of the turret frame 100with horizontal forces represented by arrow F_(x) applied to chain table3. The cumulative horizontal forces of the risers and anchor legs arerepresented by a single vector F_(x). The deflected frame shape of chaintable 3, pillars or columns 2 and turret main deck 1 is exaggerated inthe drawing for clarity. Horizontal force “F_(x)” causes chain table 3to deflect horizontally a distance “X₁” until the internal forces andmoments in the frame 100 reach equilibrium. Clearance gap 39 providessufficient space for horizontal elastic deflections of chain table 3.The entire turret frame 100 including main deck 1, pillars or columns 2(or other suitable connecting structure such as a small diameter tube),and chain table 3, contribute to the total flexibility. All of thepillars or columns 2 bend elastically while being partially constrainedby their direct connection to main deck 1 and chain table 3.

[0077]FIG. 6B illustrates the flexible nature of the turret frame whendownward vertical loads “F_(z)” and “F_(r)” act on chain table 3. Thecumulative downward force of the anchor legs is represented by thevector F_(z). The cumulative vector “F_(z)” is applied to chain table 3through the connection of mooring chain 20 and chain support 19. (SeeFIG. 5). Force “F_(z)” does not necessarily act at the geometric centerof the turret, a condition that causes non-symmetrical deflection of theframe that is not illustrated. Force “F_(z)” is transferred from chaintable 3 through pillars or columns 2 to turret main deck 1. Force vector“Fr” represents the downward force exerted by each riser 18 throughriser tube 16 onto main deck 1. Each riser force vector “Fr” may have adifferent numerical value resulting in a non-uniform distribution ofload onto main deck 1. The deflected frame shape resulting from “F_(z)”and “Fr” is exaggerated in FIG. 6B for clarity. Pillars or columns 2bend elastically in a different curve from that illustrated in FIG. 6A.

[0078]FIG. 7A is a greatly exaggerated sketch of a vessel hull in whichan internal turret 100 of the invention is installed and rotatablysupported within a moonpool of the hull. The FIG. 7A sketch shows thevessel bent into a so-called “sagging” condition such that a hullelastic curve 51 is characterized by a radius of curvature R₁, which ismany times greater than C₁, the distance from elastic curve 51 to thevessel main deck 30. From elementary beam theory it is known that theelastic curve passes through the horizontal neutral axis of each crosssection of a beam in bending, in this case, the vessel hull.

[0079]FIGS. 7B, 12, and 13 illustrate wheels 12 mounted between upperand lower rails 26U, 26B. The lower rail 26B is mounted on the turretinsert tube 5 or “moonpool” of the vessel. The upper rail 26U is mountedon a surface of the turret main deck and is positioned concentricallywith bottom rail 26B. FIG. 7B shows the turret 100 with an exaggeratedsketch illustrating the flex of the turret 100. As shown in FIGS. 7A and7B, the arrow R₂ represents a radius of curvature of the turret maindeck elastic curve 52 of turret main deck 1, while the arrow R₃represents a radius of curvature of the bottom surface of the turretmain deck 1. Since the radii R₁, R₂, and R₃ are very large, and theradii of curvature depicted in FIG. 7A all are much greater than thedistance C₁, then a common radius of curvature can be assumed for R₁,R₂, and R₃. That is,

R₁>>C₁, and

R₁≈R₂≈R₃=R.

[0080] The hull bending stress σ_(h) can be represented approximatelyas: $\sigma_{h} = {E\left( \frac{C_{1}}{R} \right)}$

${{{where}\quad E\quad {is}\quad {Youngs}\quad {Modulus}} = \frac{Stress}{Strain}},{{for}\quad {the}\quad {structural}\quad {material}},$

[0081] and predicts the elongation or compression of an object as longas the stress is less than the yield strength of the material.

[0082] In FIG. 7B, the thickness h₃ of the turret main deck 1 results ina distance C₂ from the top plate of main deck 1 to elastic curve 52. Theradius of curvature R₂, which can be represented by a common radius R asindicated above, results in a turret main deck bending stress σ_(t),$\sigma_{t} = {{{E\left( \frac{C_{2}}{R} \right)}\quad {and}\quad \sigma_{t}} = {{\sigma_{h}\left( \frac{C_{2}}{C_{1}} \right)}.}}$

[0083] It can be seen that the hull bending stress σ_(h) is greater thanturret main deck bending stress σ_(t) due to hogging and sagging.

[0084] The bottom rail 26B elastically deflects approximately in theshape of vessel main deck 30. See FIG. 13 for an enlarged view of rail26B. The turret 100 of a preferred embodiment this invention, asillustrated in FIG. 7B, is designed to have a flexibility so that maindeck 1 conforms to follows the bend of the vessel when the vessel sags(or hogs . . . the opposite of sag) so load wheels 12 remain in contactwith rail 26B, thereby continuing to distribute the vertical load to allof the wheels 12. The total deflection of the turret main frame 1 can bedetermined, because each of the deflections of the turret frame 100described by reference to FIG. 6A (deflection due to horizontal forcesF_(x)), FIG. 6B (deflection due to vertical loads) and FIGS. 7A and 7B(deflection due to hogging or sagging) are linear and can be added bythe principle of superposition.

[0085]FIG. 7C illustrates a preferred design or embodiment of theinvention where the turret 100 includes a chain table 3 with pillars 2connecting a turret main deck 1 of thickness h₃ and with the main turretdeck 1 having a central hub 32 and spokes 31 connecting an outer ring34. The hub, spoke, outer ring design of the turret main deck 1,combined with its thickness h₃ allows sufficient flexibility for upperrail 26U to flex in conformity with the sagging shape of bottom rail 26Bwhen the vessel sags. The main deck 1 flexes due to the vertical forceacting on it as illustrated in FIG. 6B.

[0086]FIG. 8 is a diagram of wheel loads distributed around a circulartrack between upper rails 26U and bottom rails 26B with a linear loadvariation that occurs with the rails 26U and 26B in a perfectly flatcondition and an external load “Fv” acting vertically at an eccentriclocation “e” from the center of the rails of the bearing. On side “B” ofthe bearing, the wheel load is a maximum of “Fw(max)” per wheel on oneor two wheels, while all other wheel loads are smaller. At side “A” theload per wheel reaches the minimum value. The wheel load is linearlydistributed along the centerline (C/L) of the vessel from point A topoint B.

[0087] The diagram of FIG. 9 shows wheel loads distributed around acircular track where the lower rail 26B has been displaced, but theupper track rail 26U is attached to a very rigid turret structure thatis in a flat plane. The lower track rail 26B has been deflected out ofthe flat plane into an exaggerated “sagging” deflection curve. Thiscondition causes the maximum load per wheel 12 to reach higher values atlocations “A” and “B” than occurs with both rails 26U, 26B in a flatplane, as illustrated in FIG. 8. Some of the wheel loads are reduced tonear zero, or some wheels may even lift off of the track, while themaximum wheel load can reach two to five times the “Fw(max)” load perwheel shown in the FIG. 8 flat rail condition. An eccentric load asshown in FIG. 9 again causes the maximum load per wheel to occur nearlocation “B”.

[0088]FIG. 10 demonstrates wheel loads distributed around circular trackrails 26U, 26B that have been deflected by vessel hull bending. Thelower rail 26B attached to the vessel structure is deflected because ofvessel “sagging”. In this case the turret structure 100 (See FIGS. 12,13) is sufficiently flexible so that the upper rail 26U tends to conformto the out-of-plane shape of the lower rail 26B due to the downwardvertical force F_(v), hereby more uniformly distributing the total loadto all of the wheels 12. This improved distribution reduces the maximumload per wheel to a significantly lower value than is the case for theconditions of FIG. 9. When the load is eccentric by an amount “e”, themaximum load per wheel again occurs at location “B.”

[0089]FIG. 11 and Table 1 below illustrate geometric proportions of theturret frame 100 that are provided to assure sufficient frameflexibility according to a preferred embodiment of the invention. TABLE1 Dimension Minimum Maximum Ratio Ratio Ratio D2/D1 1.00 1.30 D3/D1 0.400.70 D4/D1 0.15 0.25 D5/D1 0.70 1.20 D6/D5 0.60 0.80 A1/D1 0.05 0.15A2/D5 0.05 0.15 L1/D1 0.70 2.00 W1/L1 0.06 0.15 T1/W1 0.01 0.03 δ/D10.0000 0.0010

[0090] The turret deflections at rail 26U can be defined by a parameterδ, a measurement of deviation of the elastic curve from a flat plane atthe support rail 26U as illustrated in FIG. 11. Hull deflections cantypically cause a δ in lower rail 26B of about 15 millimeters with amoonpool diameter D1 of twenty-nine meters. The expected range of upperrail 26U deflections as a basis for this invention is a δ/D1 ratioranging from zero to 0.0010, where D1 is the central diameter of thesupport wheel rails 26U and 26B.

[0091]FIG. 11A provides graphs that define the allowable dimensionalratios, deflection ratios, and characteristic stress, for the flexibleframe 100 of FIGS. 11 and 7C. Characteristic stress is a numerical valuebased upon the nominal bending stress occurring in the turret main deck1 outer ring 34. A specific range of ratio of depth-of-turret-main-deckA1 to support-rail-diameter, D1, A1/D1, is required to more uniformlydistribute loads to the wheels 12 while assuring that stress is notlarge enough to cause metal fatigue failure in the turret main deck 1.Region A in FIG. 11A is the desired range of turret main deck 1proportions A1/D1 as a function of deflection ratio δ/D1 for thepreferred embodiment of turret 100. To achieve the objectivedistribution of load for the wheels 12, a preferred design requires thatthe turret frame proportions be dimensioned to allow turret main deck 1deflections that maintain at least 90% of the load wheels 12 in contactwith their rails 26B, 26U while only a fraction of the total maximumvertical load is applied to any one wheel for the turret main deck 1.

[0092]FIG. 12 is an enlarged view of the upper turret structure of thearrangement illustrated in FIGS. 5 and 7C, with its bearing system, andequipment near turret main deck 1. Main deck 1 includes outer ring 34and center ring 32 connected together by radial beams 31. Pump deck 6 ispositioned below main deck 1 and is supported by pillars 2. Pump deck 6supports chemical tank 35 and chemical pump unit 36. An assortment ofancillary modular equipment related to the fluids transfer system andcontrol system can be located on deck 6.

[0093] Components of the fluid transfer system that are supported bymain deck 1 include manifold 7, fluid swivel stack 10, and flexiblysupported piping 22. Winch deck 8 has a support frame which is mountedon outer ring 34 of main deck 1 that allows main deck flexure withoutexcessive stresses in the supports. In other words, the mounting of deck8 on outer ring 34 is done so as not to stiffen outer ring 34 or theentire turret 100. FIG. 12 shows reeving of winch wire 21 from winch 9to a centrally mounted rope sheave mounted on deck 6 for the purpose ofpulling in a mooring leg. Winch wire 21 is reeved differently to pull inrisers 18 using winch 9.

[0094]FIG. 13 is an enlarged cross section view of the arrangementillustrated in FIG. 5 showing the area at one side of the turret 100 atthe bearing and riser supports. All loads from the turret 100 acting onthe vessel 30 are transferred through load wheels 12, radial wheels 13,and uplift wheels 14. Rollers 12, 13, and 14 roll on rails 26 asillustrated in FIG. 13. Vertically acting loads are transferred throughdual concentric rails 26U, 26B to turret insert tube 5 and hullstructure 43 by means of the load equalizing effect of T-beam 27.Radially acting loads are transferred to vessel hull structure 43 bymeans of radial wheels 13 held against radial rail 26R by means ofradial spring assemblies 15. The action of spring assemblies 15 servesto distribute radial load to radial wheels 13 when bearing foundation 4is deflected out of its initial circular shape by hull deflections.Uplift wheels 14 provide restraint of the turret against rails 26B′ and26U′ in an unusual event that could cause uplift of main deck 1.

[0095]FIGS. 13 and 5 also show that the riser tube 16 is positionedbetween main deck 1 and chain table 3 and is vertically supported bychain table 3. A riser tube 16 encloses each riser 18 and providesprotection of each riser 18 from accidental physical impact from movingobjects and from accidental fire and explosion. Heat insulation materialfor fire protection can be applied to each riser tube 16 and to eachpillar 2. Riser tube slip joint 25 (FIG. 13) horizontally restrainsriser tube 16 while allowing small vertical displacements of guide tube16 relative to main deck 1. Seals 37 prevent leakage at the joint to theatmosphere of any accumulated gas from the interior of riser tube 16.The weight of riser 18 is supported by means of riser support tube 33,and riser support clamp 24 fitted onto riser end fitting 49. Thisarrangement of riser tube support does not appreciable increase overallstiffness of the turret frame. Piping connections to the risers includesafety valves 23.

[0096]FIG. 13A illustrates an alternative embodiment of riser tube 18coupling to turret 100 wherein a hanging riser tube 45 is connected toturret main deck 1. This feature is advantageous because it eliminatesthe need for chain table 3 to carry the weight of riser tubes 16 asshown in FIGS. 13 and 5. The weight of forty to one hundred twenty risertubes can be in the range of several hundred to thousands to metrictonnes. Riser tube collar 48 is fastened to chain table 3. Hanging risertube 45 is a slip fit inside riser tube collar 48, and end clearance isprovided at the bottom end of riser tube 45 to allow small relativedisplacements of the riser tube 45 relative to chain table 3. Riser tube45 is arranged and designed so that it can flex without beingoverstressed at its connection to turret main deck 1. Riser tube flange44 of riser tube 45 is supported on deck 1, and riser support clamp 24is mounted on flange 44.

[0097]FIGS. 13B, 13C, 13D, and 13E, illustrate a preferred installationmethod for hanging riser tubes 45 into main deck 1. If sufficient craneboom height is not available, riser tube 45 can be fabricated as onepiece and lowered into the slip fit of collar 48 on chain table 3 andinto its place resting on main deck 1 as in FIG. 13A. If insufficientcrane boom height is available for one-piece installation, the risertube can be installed in two or more pieces wherein a first riser tubesection 45 b is lowered through tube hole 50 to rest on chain table 3 asin FIG. 13B. Subsequently, riser tube 45 a is lowered through hole 50 torest on main deck 1 as shown in FIG. 13C. In FIG. 13D, welding fixture46 is used to clamp tube sections 45 a and 45 b together in alignmentfor making weld joint 47. FIG. 13E illustrates the completed riser tube45.

[0098]FIG. 14 illustrates winch deck 8 in a plan view (see also FIGS. 5and 12) where winch 9 is used to pull in all risers and anchor legs. Ahorizontal sheave 28, and at least one moveable vertical sheave 29,provide an arrangement for reeving winch line 21 to a point above any ofrisers 18 to provide vertical pull-in the risers. FIG. 5 illustrates thearrangement where winch line 21 is reeved through a central sheave fromwhich any of anchor chains 20 can be pulled in or let out duringinstallation or readjustment of anchor leg tension.

[0099]FIG. 15 is a plan view of main deck 1 and illustrates structuralcomponents of main deck 1 that provide the required flexibility andstrength of the preferred embodiment of turret frame 100 according tothe invention. At least three (but preferably six) radial beams 31connect and support center ring 32 to outer ring 34. As mentioned above,a single cylindrical tube (See FIG. 20) can be substituted for thepillars or columns 2, but its flexibility must be designed incoordination with chain deck 3 and main deck 1. Center ring 32 providessupport for swivel stack 10 and its associated piping. Pillars orcolumns 2 (see FIG. 5) are connected to the underside of radial beam 31near the intersection of radial beam 31 and outer ring 34. The largeopen space between radial beams 31 is advantageous for turret interiorventilation and minimizes internal pressure in the moonpool area in theevent of a gas explosion.

[0100]FIG. 16 is a plan view of chain table 3 and illustrates apreferred embodiment of structural components that provide the requiredflexibility and strength of the turret frame of this invention. At leastthree, and preferably six pillars 2 (see also FIG. 5) are attached bymoment connection to chain table 3. No brace members are providedbetween pillars or columns 2 so that a desired flexibility of the turret100 may be achieved. The pillars 2 are spaced apart to provide clearancefor pulling all mooring chains 20 radially toward the center of theturret frame. This arrangement of FIG. 16 also provides open clear spacediametrically across the interior of the turret frame, that canadvantageously be used for launching underwater remote operated vehicles(ROVs), diver entry into the water at the center of the turret, or spacefor subsea well service equipment or well work-over equipment to operateout of the bottom of the turret.

[0101]FIG. 17 illustrates an alternative embodiment of the inventionwhere a lower bearing 42 is provided to transfer horizontal load fromchain table 3 into vessel hull structure 43 near keel level. Thisarrangement is advantageous for mooring conditions where largehorizontal loads exist that tend to overturn the turret frame 100. Lowerbearing 42 comprises a plurality of lubricated individual bearing unitswhich slide on a prepared corrosion resistant surface inside turretinsert tube 5. This arrangement takes advantage of the horizontalflexibility of the turret frame 100 to compensate for misalignment andnon-concentricity of the upper and lower bearings thereby preventingconsequential overload of either the lower bearing or the upper bearing.

[0102]FIG. 18 illustrates another alternative arrangement whereelastomeric bumper pad 38 transfers horizontal load from chain table 3into vessel hull structure 43 near keel level. This arrangement isadvantageous for mooring conditions causing large but infrequenthorizontal loads that tend to overturn the turret frame. A plurality ofbumper pads 38 restrains chain table 3 when the elastic deflections ofthe turret frame exceed a desired limit such as about 100 millimeters.

[0103]FIG. 19 illustrates another embodiment of the turret frame where aplurality of riser tubes 16 provide structural connection of chain table3 to main deck 1. In this arrangement, riser tubes 16 transfer all loadsfrom chain table 3 to main deck 1 thereby making the pillars 2unnecessary.

[0104]FIG. 20 depicts another embodiment of the turret frame where asingle central tube or column 53 connects chain table 3 to turret maindeck 1 instead of multiple pillars 2 as shown in FIG. 6. Thisarrangement can be advantageous when the moonpool diameter D1 is in therange of 14 meters to 20 meters.

1. In a vessel-turret assembly including a moonpool (5) in a vessel hullstructure (43) and a turret rotatably supported within said moonpool byan axial bearing structure that includes vertical wheels (12) between anupper circular rail (26U) mounted on said turret and a lower circularrail (26B) mounted on said vessel hull structure (43), wherein saidlower rail (26B) deflects due to vessel hull structure sagging inresponse to environmental forces, an improved turret (100) characterizedby, a turret main deck (1) to which said upper circular rail is mounted,a chain table (3) separated vertically from said main deck (1) andarranged and designed for coupling with anchor legs which extend to thesea floor, and a connecting structure connected between said turret maindeck (1) and said chain table (3), said turret arranged and designed tohave a flexibility such that said upper circular rail (26U)substantially conforms in deflection with said lower circular rail (26B)when said vessel sags in response to vertical force acting on saidturret.
 2. The vessel-turret assembly of claim 1 wherein, said turretmain deck (1) includes an outer ring (34), a center ring (32), and aplurality of radial beams (31) which connect said center ring (32) withsaid outer ring (34).
 3. The vessel-turret assembly of claim 2 wherein,six radial beams (31) connect said center ring (32) with said outer ring(34).
 4. The vessel-turret assembly of claim 2 wherein, said connectingstructure includes at least three pillars (2) each one of which isconnected to a radial beam (31) of said turret main deck (1).
 5. Thevessel-turret assembly of claim 4 wherein, said upper circular rail(26U) is mounted on said outer ring (34) of said turret main deck (1).6. The vessel-turret assembly of claim 5 wherein, said upper circularrail is mounted on a bottom facing surface of said outer ring (34) ofsaid turret main deck (1), and said assembly further comprises a bearingfoundation structure (4) coupled between said vessel structure and anupper facing surface of said outer ring (34) of said turret main deck(1).
 7. The vessel-turret assembly of claim 6 further comprising, aradial bearing structure that includes horizontal wheels (13) urgedagainst a circular rail (26R) disposed on said outer ring (34) of saidturret main deck (1) by a radial spring assembly (15) mounted on saidbearing foundation structure (4).
 8. The vessel-turret assembly of claim6 further comprising, vertical uplift wheels disposed between upper andlower rails (26U′, 26B′) mounted on said bearing foundation structure(4) and said upper facing surface of said outer ring (34).
 9. Thevessel-turret assembly of claim 2 further comprising, a plurality ofriser tubes (16) connected between said outer ring (34) of said turretmain deck (1) and said chain table (3).
 10. The vessel-turret assemblyof claim 4 further comprising, a plurality of riser tubes (16) connectedbetween said outer ring (34) of said turret main deck (1) and said chaintable, where said riser tubes are arranged on two outer concentriccircles at each of said outer rings (34) and said chain table (3), andwhere said at least three pillars (2) are connected to said radial beams(31) and to said chain table (3) on inner concentric connection circleshaving a radius smaller than said two outer concentric rings.
 11. Thevessel-turret assembly of claim 9 wherein, said plurality of riser tubes(16) are mounted to said chain table (3) with each riser tube (16)including a riser tube slip joint (25) mounted at said outer ring (34)of said turret main deck (1).
 12. The vessel-turret assembly of claim 9wherein, said plurality of riser tubes (16) are hanging riser tubes (45)connected to said outer ring (34) of said turret main deck (1).
 13. Thevessel-turret assembly of claim 9 wherein, a product swivel (10) ismounted on said center ring (32), and fluid flow paths are providedbetween said plurality of riser tubes (16) at said outer rings (34) andsaid product swivel (10).
 14. The vessel-turret assembly of claim 1wherein, said chain table (3) is ring-like with an open center.
 15. Thevessel-turret assembly of claim 1 wherein, a pump deck (6) is mounted tosaid connecting structure beneath said turret main deck (1) and abovesaid chain table (3), and a chemical tank (35) and chemical pump unit(36) are mounted on said pump deck (6).
 16. The vessel-turret assemblyof claim 1 wherein, said connecting structure consists of riser tubes(16).
 17. The vessel-turret assembly of claim 9 wherein, a winch deck(8) is mounted on said outer ring (34) by a support frame.
 18. Thevessel-turret assembly of claim 9 wherein, a chain installation deck(40) is mounted to said at least three columns (2) above said chaintable (13).
 19. The vessel-turret assembly of claim 2 wherein, saidturret main deck (1) of said improved turret (100) is characterized by athickness distance A₁, said upper circular rail (26U) and said lowercircular rail (26B) are characterized by a rail diameter distance D1, apredetermined maximum deflection of said upper circular rail (26U)caused by conforming to deflection of said lower circular said (26B) dueto vessel sagging is characterized by a distance δ, and said turret maindeck (1), said chain table (3) and said connecting structure arecooperatively designed and arranged so that the ratios δ/D1 and A1/D1for an improved turret design fall within a region A defined on agraphical plot of δ/D1 versus A1/D1 where A1/D1 values are between 0.05and 0.150, and δ/D1 are below lines connecting points A1/D1=0.05,δ/D1=0.001 and A1/D1=0.100, δ/D1=0.0005; and A1/D1=0.100, δ/D1=0.0005and A1/D1=0.150, δ/D1=0.00035.
 20. The vessel-turret assembly of claim19 wherein, said turret main deck (1) of said improved turret (100) ischaracterized by an outer diameter D2, and said turret (100) is designedand arranged so that a ratio of D2/D1 greater than or equal to a minimumnumber 1.00 and less than or equal to a maximum number 1.30.
 21. Thevessel-turret assembly of claim 20 wherein, said turret main deck (1) ofsaid improved turret (100) is characterized by an inner diameter D3 ofsaid outer ring (34), and said turret (100) is designed and arranged sothat a ratio of D3/D1 is greater than or equal to a minimum number 0.40and less than or equal to maximum number 0.70.
 22. The vessel-turretassembly of claim 21, wherein, said turret main deck (1) ischaracterized by a diameter D4 of said center ring, and said turret(100) is designed and arranged so that a ratio of D4/D1 is equal to orgreater than a minimum number 0.15 and less than or equal to a maximumnumber 0.25.
 23. The vessel-turret assembly of claim 22 wherein, saidchain table (3) is in the shape of a ring and is characterized by anouter diameter D5, and said turret (100) is designed and arranged sothat a ratio D5/D1 is equal to or greater than a minimum number 0.70 andis less than or equal to a maximum number 1.20.
 24. The vessel-turretassembly of claim 23 wherein, said chain table (3) is characterized byan inner diameter D6, and said turret (100) is designed and arranged sothat a ratio D6/D5 is greater than or equal to a minimum number 0.60 andis less than or equal to a maximum number 0.80.
 25. The vessel-turretassembly of claim 24 wherein, said chain table (3) is characterized by athickness distance A2, and said turret is designed and arranged so thata ratio of A2/D5 is equal to or greater than 0.05 and equal to or lessthan 0.15.
 26. The vessel-turret assembly of claim 25 wherein, saidconnecting structure includes at least three pillars (2) and said atleast three pillars (2) are characterized by the length L1 between saidmain deck (1) and said chain table (3), and said turret is designed andarranged so that a ratio of L1/D1 is equal to or greater than 0.70 andequal to or greater than 2.00.
 27. The vessel-turret assembly of claim26 wherein, each of said at least three pillars (2) are tubular in shapeand characterized by an outer wall width diameter W1, and said turret isdesigned and arranged so that a ratio of W1/L1 is greater than or equalto 0.06 and less than or equal to 0.15.
 28. The vessel-turret assemblyof claim 27 wherein, each of said at least three pillars (2) are tubularin shape and characterized by a wall thickness T1, and said turret isdesigned and arranged so that a ratio of T1/W1 is greater than or equalto 0.01 and less than or equal to 0.03.
 29. The vessel-turret assemblyof claim 1 further comprising, a radial bearing disposed between saidchain table (3) and said moonpool (5).
 30. The vessel-turret assembly ofclaim 1 further comprising, an elastomeric bumper pad (38) disposedbetween said chain table (3) and said moonpool (5).
 31. A turret formooring a vessel comprising, a turret main deck (1), an axial bearingstructure (26U) mounted on said main deck, a structure connected to saidturret main deck, where said structure is arranged and designed forcoupling of anchor legs and risers, said turret main deck characterizedby flexibility parameters δ/D1 and A1/D1, where A1 represents athickness of said turret main deck, D1 represents a diameter of saidaxial bearing structure mounted on said main deck, δ represents apredetermined maximum deflection of said axial bearing structure, andsaid parameters δ/D1 and A1/D1 fall within a region A defined on agraphical plot of δ/D1 versus A1/D1 where A1/D1 values are between 0.05and 0.150, and δ/D1 are below lines connecting points A1/D1=0.05,δ/D1=0.001 and A1/D1=0.100, δ/D1=0.0005; and A1/D1=0.100, δ/D1=0.0005and A1/D1=0.150, δ/D1=0.00035.
 32. A large diameter turret for mooring avessel comprising, a flexible main deck (1), a flexible structureconnected to said main deck; where said structure is arranged anddesigned to couple anchor legs and at least 40 risers, said main deckand said structure being cooperatively arranged and designed such that apredetermined deflection δ results in the turret main elastic curve whensaid main deck is supported at a bearing structure mounted on a diameterD1 on a circle of said main deck (1).
 33. The turret of claim 32wherein, said flexible structure includes a chain table and riser tubeswhich connect the chain table to the main deck.
 34. The turret of claim32 wherein, said flexible structure includes a chain table and a singlecylindrical tube which connects the chain table to the main deck. 35.The turret of claim 32 wherein, said flexible structure includes a chaintable and at least three pillars which connect the chain table to themain deck.